Transmission



. R. M. *rucK :TAL

TRANSMISSION s sheets-sheet 2 Filed Nov'. 25, 1957 NN NM. www@ @ZM ,QW www d? /U m N l M. JM.. f.. ya?. @u

Aug. 20, 1963 R. M. TucK ETAL 3,101,011.-

TRANSMISSION k Filed Nov. 25, 1957 Y 5 sheets-sheet 5 /N VEN T025 Aug.2`0, 1963 VR. M. 'rUcK ETAL v 3,101,011

TRANSMISSION Filed Nov. 25, 1957 l 1 5 sheets-sheet 4 TTOENE Y Aug 20, 1963 R. M.TUcK ETA; v 3,101,011

TRANSMISSION Filed Nov. 25, 1957 5 sheets-sneet 5 eff f" A 77537K i Y n if; 24]/ f d iff v EX f77 w( 2n? y y W 'l E \\7/ 5x ffy W if? WW @a L ATTORNEY United States Patent O Sdilidlll. TRNSMESSIGN Robert M. Tuch and lames l. Mooney, Jr., Indianapolis,

and Marit E. Fisher, Carmel, lud., assiguors to General Motors Corporation, Detroit, Mich., a corporation of Belaware Filed Nov. 2S, 1957, Ser. No. 695,620 3i? Claims. ((Jl. ill- 732) This invention relates to a multiratio transmission and more particularly a transmission having a torque coni verter, a multiratio vgear unit and automatic controls.

The transmission employs a torque converter and a multiratio gear set providing three forward ratios and reverse connected in series. The multiratio :gear unit is preferably of the planetary type having a dual sun gear input and a dual carrier output. Low ratio is provided by holding the lirst ring gear. intermediate ratio may be provided by directly holding a second ring gear of this compound planetary gear set for a direct drive or by holding the second `ring gear through a one-way clutch for a Vfree wheel drive. A third ratio split torque drive is provided when the input is connected through a damping device located in the eye of the torque converter and a clutch to the second ring -gear to provide one torque path, in combination with normal input drive through the torque converter to the'sun gears to provide another torque path. Reverse is obtained kby holding the ring `gear of the reverse gear set.

The hydraulic control system is conditioned `for operal tion in low, intermediate and drive ranges, neutral and reverse range .by a manual selector valve. In the reverse, low and intermediate ranges the manual selector valve directly controls the hydraulic control system to engage respectively the reverse, first and positive intermediate gear ratios which in combination Vwith the torque converter drive provide Variable ratio drives in each of these ranges.V In intermediate range the second ring gear is positively held to provide a two-way ldrivefor down-hill braking without any speed-responsive upshift to a higher ratio. In this ratio the one-way retarding device which holds the second ring gear is also engaged but is eiectiveonly when che positive retarding device slips or is disengaged, i.e., on a shift to dri-verange, and thefreewheeling ldrive in intermediate ratio, the lower ratio of drive range, is established. Y When thespeed increases to ICC Another object of the invention is to provide in an automatic transmission having a hydraulic lcontrol system in which lluid `is supplied to a ratio change lllufid motor, au accumulator connected to the duid motor having the rate of lill of the accumulator controlled by the torque demand on the engine andthe volume of fluid in the accumulator or the pressure in said iiuid motor.

Another object of the invention is to provide in an automatic transmission having a hydraulic control system in which a source of fluid under pressure is connected to a ratio change fluid motor, an accumulator connected to the supply line and controlling valuing in the supply line to provide ilow at a high rate lduring an initial portion of the pressure rise to provide tlowat a low rate during a second pontion or" the pressure rise and to provide ow at a high rate in a thind portion of the pressure rise.

Another object of the invention is to provide in an automatic transmission having a source of pressure coni nected toa ratio change fluid motor, a valving arrangement to provide for the supply of iluids to the fluid `motor at one rate and the exhaust iluid at a different rate under certain conditions of torque demand on the engine and transmission speed.

Another object of the invention is to provide in an automatic transmission having a source of fluid connected to a ratio change fluid motor, means to supply duid to the luid motor at one rate and to exhaust iluid ing the transmission torque converter `gearing and the hydraulic controls therefor.

FIGURE 3 shows the governor and main line pressure curves.

The transmission comprises a torque converter unit `ll) and a three ratio and reverse gear unit il mounted in a housing 12. The input or engine shaft 14 is conthe upshift point lfor Lthe throttle'setting the shift valve f upshifts to engage `the clutch connecting the input to the ring gear of a second planetary gear. set to provide a split torque drive which in the converter coupling range is substantially a direct drive, Thefgovernorpressure to operatethe shiftvalve is provided by a rearfpump` Vwhose output is controlled by a multi-ple orice..gover i nor valvezto provide a stepped Igovernorcurve.y The ini put ofthe rear pump issupplied during normal operation from the 'front pump at a pressure the same as or pro-` portionate to the rear pump output pressure so that the rear pump supplies a volume of fiuid proportional to the nected by a lilex plate lo which is dished to permit relative axial movement between the engine shaft andthe torque converter housing i7. The torque converter housing car'ries the impeller blades 18 which pump fluid around the torus chamber to the tur-bine member 19 where the i fluid acts on the turbine blades 2l to drive the tunbine 17 has a central pilot v.beaning portion 34 fitting into a speed of the pump in order to provide an accurate governor pressure. The highclutch line is connected'through an accumulator to provide a controlled pressure increase regulated inaccordance with throttle pedal position for soft clutch engagement. The disengagement `of `lthe 4one- Way retarding device which `occurs -onja shift from intermediate to low range is controlled by an exhaust control valveresponsive tothrottle pressure andiigovernor pressure to provide a faster exhaust at higher speedskiand particularly under low throttle conditions. The high clutch` i,

'supply` is controlled by a timing valvewhich provides" an initial tast` pressure rise `to `till the iluid motor and*` thereafter a slow pressure rise .for soit engagement of the clutch.. Y v

Q turbine "member 19 toA reduce Vthe axial thrust.

\ The torque converter housingll' has an inner shell por-V tion '41 `attached to `the impellenblades 18 which provides' a positive drive for the split torque drive. `The shell di has a portion 42. extending overthe'stator hladeszator` providean inner shell for the stator blade and to provide member which is connected through the hubZZ to drive `the torque converter` output or lintermediate shaft 23. The fluid circulating. around theconverter torus is then redirecte-d by the stator blades "26 which aremounted on a hub `27 :connected lby theVone-way clutch device 28 to the ground Y,sleeve 29 secured by pin 3l to the housing i2.

The forward `wall 33 -of the toque converter housing bore 36 in the end of the shaft 14 to rotatably support the conventer housing. A bearing 35 is mounted within the Ibearing portion to rotatably support the turbine hub 22 andthe shaft` 23. "These Vplain `bearings permit cony verter housing 17 land pilot bearing Sriland the hub '22 to slide axially with respect to each other vand engine shaft 14. Theforward =wall of the toque converter hous-` ing 33 has a'plurality of radial Viins l38 which pump liuid radially outwardly in the `same `n:la`nner as the impeller blades 18 tovbalance the pressures on both. sides of the a semi-circular recess to receive a plurality of damper springs 43. Each pair of springs is located between a pair of abutment portions d4 on the shell 41 with a tongue 46 located between each pair of springs. The tongues 46 are mounted on a hub 47 which has a portion 48 forming the remainder of the inner shell above the stator, a strut portion 51 connected across the torque converter torus chamber having a cross section to provide the least interference with the liow of the fluid, and an inner hub portion 52 splined to the sleeve shaft 53, which as described below provides the connection lbetween the input member and the gearing for the split torque drive. The torque converter housing 17 extends inwardly to the hub 56 which on the piston 113 extend through slots lin the annularl is connected to drive the input pum-p 53 by a sleeve 57 and suitable splines permitting relative aXial movement of housing 17.

The elements of the torque converter are axially located by a thrust washer 61 located between the hub 56 and the oneway clutch 28, a thrust washer 62 located between theorie-way clutch and the hub 52, a thrust washer 63 between the turbinerhub 22 andthe front wall 33, and

thrust surfaces 64 on the hub 52 and hub 22. The hubs 22 and 52 and the Ifree wheeler 23 are respectively slidably mounted on the shafts 23, 53 and ground sleeve 29. Thus, the'parts of the converter are normally located in the position shown and expansion `of the converter housing is permitted in'either direction.

GEARING ratiodriveby a ratio engaging connecting device 72 which inv this instance is a gear reaction brake.V The ratio eny gaging device 72 consists of a plurality of plates 7 3` located between -a fixed abutment 7d-"formed vas a portion oithe Y housing 12 andra movable abutment 75 splincd to the housing 12 with alternate plates splined to ring gear '71V and intermediate plates splined to the `housing 12.y 'A fluid motor76 consisting of an E shaped annular piston 77- mounted on an L-shaped cylinder` 7S engages y'the v.

inner edge of an annular spring lever 79m swing the an-f nular leverfabout itsV outer edge which is pivoted tothe housing 12 so that an intermediate portion engages movable abutment 75 to apply the ratio engaging device The sun gear 66falso has a portion which'may be of the Asame diameter meshing withthe pinions 81 mounted on the intermediate carrier 32 which is secured bypsuitable splines Vto `the ring gearV 71. VPinions S1 ralso mesh with theintermediate ring gear` 33 vwhich may be retarded byV fthe ratio engaging connecting device d4 which .in this case is agear reaction brake.y This devicesince the reaction is, .lessVV than thereaction ontheV loweratioring gear 71 may g S6 splined to' thering gear.. 33,the fixed* labutment 87Hformed as Va portionof tie lhousing 12 and a movable abutment 88 splined to the housing AY12.* The intermediate'ratioengaging device Seis 1 actu-ated by va iiuid motor V91 having an L-shaped annular'` consist 'of one *rotatableV plate piston 92 mounted on a similar cylinder 93. [The piston f Y952 .has a plurality of thrust portions 94 engaging the mov# `Table plate 83; The annular spring lever 96 WhichmisV 1 pivoted'at'itsouter edge to the housing 12 has a plurality of lingers entendingbetweenpthe thrustportions'to retract Y thepiston. Y 'if' i Theintermediate the spring 116 to engage the end plate 111. Y. i

The split torque drive in high ratio is provided by connecting the input driven shaft 53 by `a ratio engaging con necting'device or ratio clutch 121 to a ring gear 53. .The ratio engaging device 121 has a plurali-ty of plates 122 with alternate plates connected to the housing 1533 and thus ring gear 83 and intermediate plates connected to a hub 123`formed on or connected to the input driven shaftV 53. The plates are located between the abutment 124 fixed to the housing 163 and the movable abutment 126 splined to the housing 103, The housing tifand the extension of inner race sleeve 1M cooperate to provide a Vcylinder 127 forVA the piston 12S which engages the mova-V ble plate 126. VA'centrifugal type vent valve129 opens while'pressure is being reduced in the piston 123 due to centrifugal force to more rapidly vent the cylinder 127. A retraction spring 132 located between the piston 12S and the abutment portion 133 on sleeve 162 retracts the piston.

Reverse ratio is provided by a reverse gear set which includes a carrier 136 splined to the output shaft 69 and having a plurality of planetary pinions 137 meshing with a sun gear138 connected by a hub 139' to the ring gear`71 and carrier 82 and also meshing with a reverse lring ygear 141 which may be held bythe ratio engaging connecting device 142 to establish reverse ratio. engaging device 142 consists `'of la plurality of plates v143) with laiternate plates splinedto the ring gear 141V and intermediate plates Vsplined to the fhousing 12 located between. a fixed abutment 144i on the housing 12 'and a movable abutment "146 splined Y to lhe housing` 12. This 'drive` device 143` is actuated by a iiuid motor V1413i' consisting olf a' pist-on 148 located in a cylinder 149 formed in thethousin'g 12. The piston 143 `engages the inner edge of an annular spring lever 1151 which is pivoted at its outer edge to the housing 112 and vhassan intermediate portion engaging the movable plate 146.

The rear pump 153 issuppo-rted on the rear w-alll154 i ofthe housing 12. The pump 153 may alsoV support the' APitotitube 156 located in the Pitot can v157` which is full. of iiiuid'land rotatably mounted by hub 15S 'on the output-V Y shaiftr69. This Pitot `governor "assembly may be .used toV i provide Vagovernor pressure .from Pitot tube 156 or'the V69 rat a reduced gear patio.

controlv system by replacing kgovernor line l 1677'forany accessory."` Y, ,g L .1' j. v, The low `ratio engaging device 'p72 is engaged to hold the:

eiectafl'owkratio dvethrough the-'VV Y g Vtorque `converter driven s-haftg to `drive theoutput slitut"V K 1n intermediate natiolthe ring;` L

tgelar83 is-held either'positively"byratio engaging :device f.

clutch 101 to provide free` Y Sli-'yor lthrough the `one-way wheeling drive when' only the ratio engaging device 107 V--is employed. When the ring v'gear 631s held thedrive is ratio` also be established through i:

one-way clutch` 101 which lhas an inner race sleeve 102.V

connected by :a clutchV housing 103 "splined ,tofabutment g 1124 Welded to theyring'igear 83.f V,The one-wayl clutch-'has vYan `outer race 104'formed vas a portion ofthehub 1166" Y whichlmay be retardedxbyaratio zengaging' connecting? ,device 107Y which consists'of a plurality of plates 1&3 with i Valternate platessplined to theziiuoriti and intermediate through' the torque converter to thetorque 'converter out? j put shaft 23 and sun gearo 'whioh rotates the planetary carrier SZand rngigear-71 rattan intermedi-ate speed VsoV thatsun' gegar' driving-the pinions 6|a nd carriene in', gear 71 rotates the output conjunction withaa moving ring shaft 695at van interjmecli-'ate speed.

4YI-ligh' ratio drive is a split torque drive-with part of the -powerjor torque iliow passing through the torque converter byfithe'actionjof,the'inipeller'bladesfl andthe 'turbinei blades 21`tot`hef oonventer output shaft 23 and partotthe 'f povv'erpassingV bydirect meohanioai .connectionQ-fronithe,

` input shaft 14,'converter housing 17 and thedampingl `device locatedpin the eye ofthe torque converter housing The ratio drivel l The super charger valve` 1173A? has the val `havinglands aand bof equalgdiameter loo to Ithe direct drive shaft 53. The torque converter output shaft 23 drives the sun gear 66, `and the `direct drive shaft 53, when the ratio engaging device 121 is engaged,

drives the ring gear 83 to provide a split torque drive substantially at l to l ratio when the converter is operating in the coupling range.

Hydraulic Control System The hydraulic control system is manually controlled to select neutral, low, intermediate, drive or reverse ranges of operation. In neutral all rhe ratio engaging devices are disengaged so that torque cannot 'be transmitted to the output. In low range a loW -gear ratio is engaged by the ratio engaging device 72. In intermediate range a positive second lgear ratio is engaged by the ratioengaging devices 34 md 107. In drive range, :a reeWheeli-ng drive in second ratio is provided at low speeds by the ratio engaging device 107 `and a split torque substantially direot drive is provided at high speeds by engaging ratio engaging device 121. In reverse range the reverse ratio is engaged Iby the ratio engaging device 142.

The hydraulic control system is supplied from a uid sum-p, FIG. 2b, normally located in the lower portion loi the transmission housing lay line i161, iilter 162 and pump supply line 163 to the front pump 58. The pump supply line 163 is connected through a one-Way check valve 164 to rear pump 153. The iront pump 58 supplies fluid to the front pump line 166 While she rear pump 153 supplies fluid to the rear pump line 167.

Push Start Valve Whenever the engine is running to drive the Afront pump 53, the front pump pressure in line 166 moves fthe push start valve 168 (FIG. 2b) to the drive position connecting iront pump line 166 to the main line 169 and rear pump line 167 to the governor line `1'71. When the engine is not running and the lfront pump is mhus not supplying fluid, the push start valve 168 is in position shown in FGURE 2b connecting the rear pump line 167 to the main line 169. The push start valve 168 has a` valve element 173 having equal diameter lands a land b located in a -bore y17d which is vented at th'e end adjacent land a and closed at `the end adjacent land b. A spring 175 located in one end of the bore acts `on land a of valve element 173 to urge the valve from the drive ltoward the push start position. With the valve inl this position the rea-r pump line 167 is connected to the bore `17 4 yadjacent land a and communicates through the bore with the rnain line 169 which is: connected to the` :bore adjacent land b. t Thus, during apush start the rear pump supplies uid via line 4167 through the push start yvalvea168 to the main line 169. `With the valve infthe push start position governor the bore to a'branch of line 165 connected to the bore 182' adjacent land b. The valve element 181 is thus balanced between rear pump supply pressure rfroin line 165 acting on land a which tends to rnove valve element toward the closed position and `governor pressure from line 171 acting on the end of land b :which tends to move the valve to the open position shown in FIGURE 2b in which the front pump supply line is connected to supply uid to the rear pump supply line 165. When the pressure in the rear pump supply line 165 is equa-l to governor pressure or slightly exceeds governor pressure the valve element 181 will move 'and land a will close the connection between front pump line 166 and rear pump supply line 165. When the governor pressure in line '171 exceeds rear pump supply pressure in line 165 the 'governor pressure will act on land b and move the valve to the open position permitting additional supply of lluid `from the front pump by line 166 to rear pump supply line 165'.

Governor Valve The governor valve 186 in FIGURE 2b connects the governor line 171 to a series of orifices to provide a stepped ygovernor pressure (as shown in FIG. 3) proportional -to output shaft speed in governor line 171 and 4rear pump line 167 when connected by the push start valve 168. '111e governor valve 186 has a valve element 187 located in la bore `18S and urged by spring `189 to the first stage position shown where the valve 187 abuts stop `183. initially a branch of the governor line 171 is connected to orice exhaust 191 to provide the first pressure rise Stage proportional to output pump `and shaft speed. When the governor pressure in line 171 reaches the first step: the lvalve element 187 moves against the spring 139 to open the second orifice 192 to provide a pressure riseproportional to output shaft speed. At the end of the second stage or at the second step the valve element 187 will have movedsufliciently to open the third orice 193 and the governorpressure will again level oit and then rise proportional to increasing output shaft speed during the third governor stage. The spring chamber portion of bore `181i is providedwith an exhaust 4194i to `prevent accumulation of uid which would interfere with the operation of valve `11"'.

This arrangement provides e. stepped pressure rise curve 196, as shown in FIG. 3 atfull throttle in drive and intermediate ranges when the( mainline pressure varies in accordance with curve 234: f

Since the mainline pressure is reduced as explained v below with decreasing throttle to the pressure curve line 171 is connected to exhaust through the lvented bore 174 lbeyond land a. When the front pumpsupplies fluid via line 166 to the olosed end of the bore 17'4l beyond 'land b the uid moves the valve against spring 175 to .the drive position connecting the iront pump line 166 to the main Y The rear pump super charger valve 173-1-,(FIG.2b), when the engine is running, supplies fluid from lthe front pump at apressure equal to the governor pressure in gov` ernor1line171 co Asuper' charge the rea-r pump 153 so that 1 Vthe inletpressure` and the outlet pressure .aresubstantially equal -andtheoutlet pressure is proportional `to the Vspeed of rotationl ofthe rear pumpy to provide 'a ygovernorVpres- A" sure rnoreaocurately proportional to putpulshaft speed;v

'element .11811 i 7o isurged to the closed position .fbyspri l land a and located in azspring. chamber 8.ooaxial with i the'bore 202? so that th`e .lai 1d'e engageshthe` closed end of bore 205. Al sleeve1elem-ent` 211 located inthe spring `chamber Zlltlma'y" provide a seat for' the spring` 2351^at` closed throttle, and' since valve 199 prevents the' governor. pressure from exceeding main line pressure the terminal por-tion of the governor Acurve 195 at closed throttle `in drive and intermediate ranges Vis `flat and coincides with main line pressure as shown in FIG. 3.

Main Regulator Valve The main regulator valve 19S shown in FlGURE 2b controls the pressure in main line 169 at a lregulated pressure which varies in accordance with throttle pedal check valve `199 permits liow `only from the rear pump y line 167 Ito the main line 169 to prevent rear pumpfor,

governor pressure exceeding the main line pressure. The

`regulator valve 198 has a valve"elementfZQLhavingf'f "lands a, b and c of'equal diameterflocated in a b,ore.

202 `and lands d and! e" havingsuccessivelylreiluceddi-A t ameters Vlocated in coaxially bore` ',portions204 and f' 2115 3 having corresponding diametersff-5'lhevlve element i111 297 abutting.

V207 andVv has a -valve'plug vlands d and e.

212 located in a bore 213. Throttle line 215 supplies a pressure proportional to throttle pedal position as explained below to the bore 213 to act ion the plug 212 to assist the spring 207 to raise the main line pressure with increasing throttle pedal position. Spring chamber 2th?) is provided with an exhaust 216. Main line'169' is connected through the valve'lbetween the lands b and c in all valve positions. The branch i217 of the main line 169 is connected through a one-Way check valve 218 between the bore portionsV 24M- and l265 to act on the unbalanced area between the The line pressure from branch 217 acting on the unbalanced area between lands d and e tends't'o move the Valve element 2111 to the open position against spring l207. As the 4valve Zildmoves Vtoward theV iopen position land b first uncovers the port for the conyerterline 221 which is connected through an orice ,222 tothe space between the ground sleeve 29 Vand the sleeveV shaft 53 andl Iafgroove' 223 in the hub 52 to the torque converter chamber. "The outlet from the torque converter chamber passes through radial groove y224 in hub 56 and between the drive sleeve 57 and the groundV Vsleeve 29 to outlet line' 226 which is connected to they vcooler 227. The cooler outlet line 22d in which pressure is regulated by the regulator valve 229 is connected at the rear of the transmission (FIG. 2a) to an axial lubricating passage 231 in shaft 69 having a plurality of branches connected to lubricate the transmission gearing. Regulator valve :198i first supplies fluid to main line 169 then supplies excess fluid to the converter line 221 and regulates the pressure in both of these lines `when supplied at the same value. On an increase of pressure above the regulator valve, ,the land a of valve Y element'26i1 will move out of thef'lbore 292 and connect a branchof'the front pumpline 166l which is always connected to the bore-2% between the lands a and b l 'through the bore 202 Vto the spring chamber 2113 and exhaust-216 to directly Vent the front Vpump without having uid pass through the push start yvalve 16S or regulator valve-19'8. The intermediate `and drive range 4' line ,-219 which is supplied ,with fluid under pressure in intermediate and drive rangesV as explained below is Vcormeeted tgo the valve 1% between the bores 292 and `204v and acts on the unbalanced area between the lands 'cf randd to reduce the regulated pressure during opera-V ;tion of( the transmission in intermediate and driveranges.u The governor-line 1711s connected .to the Vend oibore 205 and .acts on land elto reduce the regulate'dma'inzline Y Throttle Valve A Ihema'in line is connected to the throttle lvalve 236 f f (FIG. 2d) Whichprovides a pressure in the'throttle line 215ovra range of part-throttle Vpedal positions substaritially.V proportional to Vthrottle Vpedal positionerid a- Vpressure in detent line237 substantially equal to ,f l'inejpressure-when the throttle pedal Aposition is: at the -full `throttle' position orclosely `adjacent thereto in acfcordance-with the4 operatorfs positioning of the throttle V Thejjthr'ottle"valve"'236 includes a throttle' Yregni' IVE ,elementi-1S, hvlafa large ,land` a vlocated getafe/'13 dienaar/sadness a and c located f l nd a `hrottlef detent -valve element 2435 d i `qualfdia'rneterlocatedin bore'l fand`A c Ending 'into :borsetta TheA Ais'actuated'.'byr 'a lever 2,66 whichV 1 .Y fr *Y y *,Thejdrrye vrrela'yjfvalve 129j1`conn'e'cts :eitherV the inter-p-l nediateiclutchgline 4273er thevrv drive-frange' linel2fk72itd "fthe, in e'rmediatev and drive `ra"ngeflinejg219 without 'in-" terconnecting the v, interrnediatev` Aclinch lineA l/ariygl drive'lf` 'moves with `the,.-tl'irottle pedal andacts fon the end `of pressure in steps inverselysimilar to Athe increasing gov-t j ,ernor pressure as illustrated inthe curves 23d and 235 FIG.- 3 respectively 1for full Vand closed throttle in ment 243 compresses spring 247 `between the` valve ele- Y ments to increase the spring force acting on the regulator valve element 238 to tend to move the valve against the throttle pressure in bore 241 to open or connect main line 169 between the lands b and c to the throttle line 215 yand close exhaust A24th. Fluid is quickly supplied from throttle line 215 through the branch 251 having one-way check valve 252 to 'the kclosed end of the bore 241 to act on the land a of valve element 23% to oppose the force exerted on valve element 23S by spring 24117k exhaust |255 at the middle. of landb prevents excessive' leakage of fluid between the bore 241 and the main line port 169. The exhaust 257 always exhausts 'the space between the valve elements 238 and 243 to prevent accumulation of fluid which would interfere with the valve notion and in the closed throttle position shown exhausts the detent line 237. When the detent valve element 243 reaches substantially full throttle position Vthe throttle line 215 is connected by branch 25S between the lands a and b of valve element 243 to the detent line 237 to supply substantially full line pressure to this line. If the high ratio clutch is engagedV so that the transmission can be downshifted, the movement of the detent valve element 243 in the detent downshift or full throttle position is hydraulically resisted. Fluid at main line pressure in the high clutch line 3h31 is connected to the unbalanced area between the lands b and c of Valve element 243 just after the land c centers the-bore 2744 to provideV a hydraulic force resisting `movement of l the Valve element 243 to providel a signal to `indicate to the operator by'ran increased resistance to'rnovement of the throttle pedal that a detent downshift is being made.

' The shoulder' 261 limits movement to the valve element 243 inthe bore.

t Manual Valve YTheV manual valyfeZG connects the main line 169 in reverse range R to the reverse clutch line 27-1',` in driveV range DR to the drive rangeline V272, inintermediate range INT to intermediate {clutehl 'line' 27 3,.'andl inflow i range LO to the low clutch line 274. The'valve`266 has an element 276 having lands a, b, c andd o'equal diameter located ina bore `277. 'A series of annular grooves 27'8 floc'ated between the ,lands vb and e cooperate with Va detent `279fto resiliently positionthe valve in eachof4 the range positionsR, N, DR, `INT and LO. The mainl other rangeppositions DR, INT and LO connectsV the j line169` is connected to thev bore 277 between the lands a "andJb-in all positions of lvalve'element 276, and thus iscontinuously connected by ports 281 anda central boreV 2?21through1the valve element 276- tothe space `between the lands o and d: In the reverse positionl illustrated the space between the lands c and is connected to the Vreverse Aline 271 to supply uid to reverse ratio engaging device 1112.V 'Similarly moving the valve to the space be'tweenthe-lands cfand d to supply iluid respectively" to. drive r'angewline 2272, intermediateline 273".

and lowline 2.74.- Inf' neutral the space` between' the.`V

."lands'ifc'and'djis =.block`e d. "ln all positio not connected to" the main llineA '169 lby the spaee between the "lands'jcand Vd are `exhausted viaexh'aust 2861013287 'the lines,

range line, so that in both intermediate and drive range positions of the manual selector valve, main line uid is supplied to the intermediate and drive range line 219. The drive relay valve 291 has a valve element 292 located in a closed bore 293 and a spring 294 seated lat one end of closed bore and engaging the valve element 292 to urge the valve to the position connecting the drive range line 272 to a branch 296 of the intermediate and drive range line 219. In this position valve element 292 blocks communication between the intermediate clutch line 273 and either intermediate and drive range line 219 or drive range line 272. When the manual valve is shifted to intermediate position main line iluid entering intermediate clutch line 273 enters the closed end of bore 293 and moves the valve element v292 to the intermediate position against the force of spring 294 connecting intermediate clutch line 2173 to intermediate and drive range line 219' and blocks branch 296 so that the drive range line 272 cannot communicate with either line 219 or line 273.

Intermediate High Shift Valve The intermediate high shift Valve 293 controls the automatic upshift in drive range from intermediate ratio to high ratio in accordance with output shaft speed and throttle pedal position. The intermediate high shift valve 298 has a Valve element 299 having lands a, b and c located in a stepped bore Sill. Land c has a larger diameter than land b and is located in the larger portion of the stepped bore 301 to provide Aan unbalanced larea acted on by the high clutch iuid for the hysteresis action which delays a downshift. The bore is closed at the end adjacent land a and connected to the rear pump or governor line 167 so that governor pressure acts on the end of lland a to urge the valve from the intermediate to the high position. Alternatively the Pitot governor may supply the governor pressure through line 160. 'Ille space between the lands a and b is connected to the exhaust port 302 to prevent leakage high clutch line 303 is connectedbetween the lands b and c to exhaust 394. When the valve element 299 moves to the" high ratio position the exhaust 394 is closed by the land b land the drive range line 272 `is con# nected between the lands b and c to the high clutch line 393.` `A partwthrottledownshiit plug 307 is loca-tedin a reduced coaxial portion 398 of the bore l301 and `acts" on the V-free end of the landV c of valve Velement 299. SA rear pump plug `311 is located in a-`s`eparate bore 312 located 4coaxially with respecttothe boresli Aandkjiitll"A and has a stem 314,Aproje'ctingfthrough 'anfaperture'in the wall 315 between thelbores ilt2fand`1tl8,` engaging the plug3tl7l` `Aispring 316 abutting the closed end of bore 312 and the vented endfofithe bore312 engages the plug 311 to urgefthe downshift plug' 367 andthe Valveelement 299' to theintermediatetposition. The

Y springchamber end of bore 312 is vented by exhaust 317.

VVThe. spring 316 normally maintains all of the valve elements, the rear pump plu-g I311,A the downshift plugl i 3017 `and the valve element 299 in the :intermediate or downshift position. The Spring and the valve areas are calibrated so that when .the vehicle `has reached a4 speed at which it isfdesired `to provide zero `throttle upi shift the governorlpressure inthe linet157` actingon the- Hplng 311 and onithe land a of valvefelement 2979 will` i exert asu'icient force "totupshift .the valve againstthe- -t-,vforcegof spring"316.tof the high ratio` position. u This type of shift willlalsolo'ccurfat certain part throttle. ipositionstabnorrhallyi)loriV in comparison to. the vehicle j speed. The throttlefpreslsure line215 is conr` i"eeted"sfo. iluid acts on the land cA gifyalve elementrf29 "to movetheV vvalve toward theintermediate.positionagainsttlie glov- .einer vpressurefrom` line :167 actingv onland at the l i pedal position. lThe intermediate drive ratio line 2119 also 10 other end and acts on the stem 314 of rear pump plug 311 to move the plug away from the plug 307. At certain part throttle positions with the vehicle under way at a speed in the normal range for a particular part throttle position, the throttle pressure kacting on the stem 314 andthe governor pressure acting on plug 311 is snlicient to move the rear pump pl-ug 311 down against the force of springs 316 to a disabled position disengaging the spring 316 from the valve element 299` to condition valve 299' for rateless shifting. Lt will be apprecirated that throttle pressure acts on both ends of the plug 397 and thus exerts no force ton this plug. At this time the throttle pressure is suicient to oppose the governor pressure and hold valve 299 in the downshitt position. Thereafter with increasing speed the governor pressure acting on land a will upshift the valve element 239 against lthe force of throttle pressure acting in the op'- posite direction on land c as a rateless valve. Lands b and c have a small unbalanced area tending to hold the valve element in the upshift position to provide hysteresis. Also, after an upshifit, land c of valve element 299 closes the port of throttle valve line 215 to the space between' land c and part throttle downshift plug 367. Since throttle valve iline 215 remains connected between plug 307 and stem 314, and part throttle downshift plug has #less area than land c, there is a reduced throttle force on the valve 299 after upshift. At full throttle, line pressure supplied through the forced downshift line 237 enters the bore 301 between the plug 307 and the land c of valve element 299 to move the valve to the downshift position against the governor pressure.

Accumulator piston 326located in abore 327 and is urged by springs 328' toward the discharge end 329 of the bore. The intermediate drive range line 2119 is connected through a check valve 331 to the dischargeend 329 of accumulator bore 327 and to the freewheel line 322. The accumulator piston 326 has a projection valve actuator 332 lwhich when the accumula-tor is in the empty position as sho-wn in FIG. 2d holds the check valve 3311 open for `unrestricted iiow from lines 219` to 322. As soon as lthe accumulator is partiallycharged the piston 326 is raised sufficiently so that'the check valve 331 closes and further flow from line 219 lto fthe acumulator and line 3122 must pass through `a small orifice 333 in the check valve 334 which now closed. l The tlow. then `continues through a larger orice 335 which -does `not control the ow to the accumulator bore 327 and vline 322.

Throttle line 215 is `connected to theclosed end 337 of the accumulator to assist the springs to vary aipressure def livered by the accumulator in accordance"with throttle has .a branch 33S connected to the `accumulator bore327 at a point so that it is blocked unless the accumulator is in itsfsubstantiaily fully charged position. A Thus, when the accumulatoris .fully. char-gedan unrestricted connection is established between line 219 through'ibr-anch 338 and 'the aocumulator"=bore 3271*-to3`li`r1'e322. On emaust during disengagement of the tfreewheel intermediate ratio engaging device,` the` exhaust V1will, `when the exhaustvcontrol Valve @l is closed, ilow through A`line322` and during` a 'rst `inp stant'exhaustrlfreely through branch line 338an`d the inter-r v `mediate drive range line 219 to exhaust. Then `'ais the l f piston SZE'closfesrtheport to branch line` 338 the check 75,

valve"331 :will open at `a flow pressure so that the large Exhaust Control Valve The exhaust control valve 341 shown in FIG. 2a controis the exhaust `front the yfreewheel intermediate ratio engaging device '167 in accordance ywith throttle pedal position and output speed. The exhaust control valve Sdi has a valve element 342 having lands a, b and c located in a bore 343 having a small Vdiameter portion 344 for land a and a lar-ge diameter portion 546 for lands b and c. A spring 347 abutting the shoulder between boreportions 344i and '346 engages the land b to urge the valve toward the closed end yof bore 346. The governor line 167 is connected .to the closed end of the bore 346 to act on the end of land c to move the valveagainst the force of spring 347. The throttle -line ZES Iis connected tothe closed end or bore 34d to act on the end of the land Zz to Vr'n'ove the Vvalve lwith the spring. The spring chamber portion of ybore 346 is provided -with an exhaust 34S adjacent horc portion 3414. The valve element 342 is illustrated in the closed `or low speed position with the land I) blocking a hranch of the treewheel drive range line 322; so that the exhaust from the ratio engaging device 167 i'loWs only through the line 322i and not through -line 323. At higher speeds varying upwardly with increasing throttle pedal position the valve element 342 will -be moved against spring and freewheel intermediate line 3221 will be connected between the lands b 'and c to the freewheel intermediate exhaust line 3213 which passes through a Asmall orifice 351 and through the one-way valve 324 to the line @i9 at exhaust in parallel with the normal exhaust flow through vline 322 and orifice 335 to provide a faster exhaust.

If the valve 341 is open during engagement of the freewheel intermediate ratio engaging device lil it will not be supplied through line 323 since thercheck valve 321% will Vprevent flow Vin this direction.

High Ratio Timing Valve The high ratiotiming valve 354 provides a -ast fill ofthe higlr ratio fluidfrnotor for the split torque ratio engaging device [121 during an initial low portion of the pressure rise, :approximately sufficient to till the iluidjmotor, and thereatter provideV a `slow till to retard the pressure'rise during engagement ofV the ratioengaging device.Y This timing valve 3S4'consists oa valve element 35d having lands a and Vl? ofrequaldiameterxlocatedan |ar bore 357. Afspring 3755 abutting one end of thevalve bore having exhaust 359 engages the land 4a to V'moveV the valve element toward the fast till position. In this position the high'VV A clutch' line 'illTa-is` connected through a full ilow,*brancl'i-y through line 273, this4 cushioning has noeifeot on Avthis Y the cooler 227 and lubricating passages 231 for the transmission gearing. The manual valve 266 may then be shifted from neutral to the range positionsindicated below to'establish the ratios X `as shown in the following table and described below.

Ratio devices R Reverse Y. d Low Range, `Operation ln'low range t to the L@ orlow range positionindicated in FIG. 2c in `which the main line i@ having the regulated pressure is connected to the low clutch `or range `line 274- Which supplies iluid to the 4low ratio engaging device 72. for manual control of low ratio. The other range lines are .then connected to exhaust 236 or 287. Y

intermediate Range permion `The line 219 is connected through the. accumulator'Zl i and associated orices to intermediate freewheel` drive line 322 to cushion the engagement of the freewheeling ratio device llt during a `lovvrtol .thighl rangey shift as' fully explained below. Since the/engagement gnithetreewheel-V inginterniediateratio engaging,device-167? does not effect the' operation of the gearing on ashiftfrom lowftointer-`v 1* niediaterangehecause the direct drive intermediate ratio u engaging device 'Se isfirst eugaged'by unrestrictednow shift.

' However,V on'a shiftfronr intermediate tollcw rangetlie Sotto the highvmotorline 3621.- Highmotorzline-is also connected to the closed end of borei'?V to act on the free end of land b of valve element 356 yand at an intermediate lpressure lshortly after thehigh ratio engaging iluid nio-tor device .is filled and the pressure therein is just suflicient to initiate movement to `(move the valve element 356, against i spring V35, to the restricted position in which land b.V "blocks-owto thefree branch 351 and only permits iiow from line 363 through restrict-ed orice branch 363 to line suicient v-force to provide an exhaust pressure yin lineo,

' dur-ing iiow through-the' orifice 363, to provide sufficient restricted position so thatV pressure to hold the valve' in the operation. g when massime' is regulated by regulator valve 1% rst to the main line 169 in converter line 2.2i

p y v.tained its" drive ,theiinptir member orengine;shaft Iliffthe pumpr supplies fluid tapressure manual selector-valve svvill be moved Vto the LO plosi- Y i tionrventingyline 273 at'the manual selector valve. Flfhe funrestriotedvent itlirough'ithe :intermediate range vline 27 3V Vwillfirst' di'sengage .thedire'ct driveintermediateratio en- 60. k362 to supply the high ratiovv engaging ldevice.- The re'- ,traction springs -for the `high ratioV engaging device have Y "intermediate 'treewheel drive,v and lsplit torquehigh :ratio 'drive Vl/henrtl'ie manual yserle'ctgw'or valve 2 66 is'nioved l"to v freewheel intermediate v'ratio[device in? Ywill remain ing intermediate ratio'engagingdevice1li? through the line ate ratio devicek in 'ligh'tlyengaged.l This uslowe'xhaust will provide [overlap Vfor the 'intermediate to' low range shift. Since'this shift isusually made at lowspeedslthe' exhaust control valve deiV willf be` closed further delaying theshift.- Y Dll'vejRnnge `Operation lIn drive'r'aiigean autrna'ticjs is provided be the drivefrange position mainline 169 wil-libe Aconnected Vot the drive range line 2172y supplying-'theintermediateihigh-f kshift,vlalvev w chwouldnorrnallyh vinthe `ovvnsh f' positionfsh'owmjb cking line A27 I t' ne'cted throughsithf Y i. drive range' linegzilQ rele-xref ne manual selector valve 256 is moved `trolled by the tim-ing valve 354.

On a downshift from drive range to loW range with the Y 13 gaged as intermediate clutch line 273 is disconnected and drive range line i272 connected by drive relay valve 291 to intermediate drive range line 219. Valve 291 changes these connections quickly Without any appreciable loss of pressure in ratio device 107 and any loss of pressure would be counteracted by the accumulator 321.

Since the freewheeling intermediate ratio engaging device 107 is not engaged in low ratio, it Will be engaged on a shift from low to drive range to pick up the drive during engagement. This engagement is cushioned by the accumulator and associated orices.

When the manual valve 266 is moved from low range to drive range the low ratio device 72 is disengaged by exhausting low clutch line 274 'at exhaust 237 and connecting main line 169 to drive range line 272. Drive range line 272 is connected to the intermediate high shift valve 293 which in the low speed position shown blocks the ow and is connected to the drive relay valve 291 which connects this line to the intermediate drive range line 219. This line 219 is connected through the accumulator 321 and orifices to the intermediate freewheel drive line 322 to cushion the engagement of the intermediate freewheel device i107. Initially while the project-ion 532 on the accumulator piston 326 holds the check valve 331 open, an unrestricted connection is provided from line 219 through valve 331 and line 322 to quickly fill the fneewheeling intermediate ratio engaging device 107. At a predetermined low pressure sufcient to initiate engaging movement of intermediate ratio device 107 the accumulator piston 326 rises so that the projection 332 permits the check valve l331 to close. Thereafter iioW continues through the ysmall :orifice 333 to ll the accumulator slowly to complete the engagementiof the ratio engaging device 107 at a very slow rate with a slower pressure rise. After this ratio engaging device 11W is fully engaged the accuo mulator Will be raised to permit unrestricted connection between branch 33S of intermediate drive range line 219 to the accumulator bore `327 `and line 322.

When the transmission is operating in drive range an increase in speed lor a decrease in throttle position may shift the intermediate high valve 2918 =to place the transmission in splittorque high ratio. As explained above the valve element 299 of shift valve 298 will upshift at a certain speed under closed throttle conditions against `the spring 3:16 and the spring under certain part throttle or high speed conditions will be disengaged from the valve `so Cil 14 ratio will be downshifted to the freewheeling intermediate ratio and then to low ratio.

On a shift from drive range to intermediate range, the drive range line 272 is exhausted at the manual valve. if the transmission Was in high ratio, the device 121 would be exhausted via line 362, timing valve 354, high clutch line 303 and line 272. The intermediate clutch line 273 would be supplied at the manual valve to engage the intermediate direct drive device 84, and actuate relay valve 291 to supply line 219 to continue the engagement of the freewheeling intermediate ratio device 107.

Reverse Range Operation For reverse drive Ithe manual valve 266 is moved to the R or reverse position connecting the main line 169 to reverse line 271, the other range lines being connected to exhaust 287.

The above described preferred embodiment is illustraf tive lof the invention which may be modified Within the scope of the appended claims.

We claim:

1. In an automatic transmission; 'an input member; an output member; drive means including a first drive providing two-way torque transmission having first iluid operated means operative for engaging said first, drive, a second drive providing only one-Way torque transmission having second fluid operated means operative for engaging said second drive,` and a third drive providing torque transmission having fluid operated means operative for engaging said third drive; each :of said drives connecting said input member to said output member to drive said .output member in the same direction; said first and second -drives havin-g the same speed ratio and said third drive having a higher speed ratio; a source of iiuid under pressure; valve means for connecting said source to said flrstand second fluid operated means to engage and disengag'er said fir-st and ,second drives and being operative in a first position for controlling the supply of iluid yto said first and second fluid operated means for disengaging said rst and second drives and being operative in a second position `for ycr'introlling the supply of fluid to 'said first and second fiuid operated means -for engaging said rst drive -and including time delayrneans operative for controlling the supply of fluid to said second uidoperated means for Vengaging said sec-ond drive 4a predetermined time `after engagement `of said rst drive that the upshift due to the opposing governor and throttle p forces `will be rateless since the spring does not act onthe valve element 299. When the valve upshifts the drive Arange Aline 272 will be connected betweenthe lands `b and c to the high clutch line 393.

The rate of engagement of the split torque high ratio engaging device 121 will be controlled bythehigh ratio timing valve 354 `as explained above to cushion ,the shift. `After a high throttle dovvnshiftdue .to a reduction in speed or a detent dovvnshift line 272 `would, be blocked by land c andthe high ratio line 303 connected to exhaust 304. This exhaust `as explained above is contransmission operating in high ratio, the high clutch will be exhausted via line 272 `and the manual valve. The freevvheeling intermediate ratio engaging device 107 and accumulator 321 Will be exhausted through line 322 and orifice 335 or'at higher speeds `also through exhaust con trol valve 341 and smaller orifice 351 and then in` either case through line 219, relayvalve 291 and line 272 to the exhaust'at :themanual control-valve 266; {Th'e disengagement of the intermediate ireewheel device 107 `will be delayedldue to thej additionalfluid -supplied by theac cumulator 321,the restriction'of the orifices and Ydue to the fact thatl the exhaust must flow through line 272 carry'- ing the high clutch exhaust. Thus, on af shift from :drive i `range to low range the transmission'if `operating in Vhigh -said first andsecond drives `lhaviiig thesame spec and being operative in a third position for controlling the supply of fiuid to said rst and :secondfiuidactuated means to disengage said rst drive and `to engage said second driverand means `for controllingfthesupply of fluid to said third drive for engaging and disengaging said third driveA operative',V only Awhen said valve means is in` Said` third `position to controlV the supply of fluid to` said i `third fluid operated means to engage said thirddrive.

2. `i`he invention dened in claim I1 and a `regulator"` valve to regulate the` `pressure of said source and means.l .s operative on movement'of said" valve means to said secy ond position to `reduce they pressure regulated by said regulator Vvalve prior to establishment of said second drive. i p f 3'. In .an automatic transmission; an input member; )an output member; drive means including a firstdrive providing two-Way torque transmission having irst fiuid `operated means operative for engaging ,said firsttdrive, a second drive providing only one-Way torque.transmis-I sion having second fluid operated means operative `for i Vengaging said second `drive and a third drive providing twofway torque transmission having fluid operated means operative. for. engaging said. third `ydrive; -each offsaidv drives connecting saidjinput member ,tosaid outputmem, i .om I.

ber to drive said loutput member, 1`in'7the same` di and saidwthi'rd drive having a higher speed ratio; a;

rce v` i' of Vfluid under pressure; controlrn'eans includingv valve `saidfirst-andsecond v f aranci;

fluid operated means operative in a first position for exhausting said first and second fluid operated means to disengage said first `and second drives and movable to a second position for operation for supplying fluid to said first fluid operated means to engage said first `drive and including time delay means operative `for delaying the supply of fluid to said second fluid operated means to engage said second drive a predetermined time after engagement 4of Vsaidy first drive, 'and being operative in a third position for exhausting said first fluid actuated means to disengage said first drive and for supplying fluid tosaid second fluid actuated means to engage said second drive; and means operative only When said valve means is in said third position for controlling the supply of fluid Atogsaid'til'fird fluid operated means to engage said third drive; t Y Y f 4. Therinvention `defined in claim 3 and said con-trol means also including orifice means controlling the supply of fluid from said source to saidsecond drive fluid operatedrneans to provide `a restricted passage during Vat least l a portion of the pressure rise in said'second drive fluid operated means yduring establishment Vof said second drive.

5. The invention detlnedin `claim 3 and said controlY means including means to control the exhaust of said second freewheel drive device on disestablishment to in-Y crease the rate-of exhaust of fluid -athigher transmission speeds. t

6; The invention defined in claim 3 and said control means including an accumulator connected to said second drive fluid operated means and variable orice means controlling the supply of fluid from said source to said second "drive fluid operated means ,controlled by said accumulator. f

7,. In Vanfautomatic transmission; an input member; an output member; drive means including a first drive pro` viding `tvvo-vvay vtorque;"transmi,ssion having first fluid operated means 'operative for engaging said first drive, a second drive providing only one-way torque transmission having second fluidyoperated means operative for engaging saidsecondV drive, andra third drive providing Vtwo-Way torque ltransmission having fluid operated means operative for engaging said thirddrive; each Vof said drives connecting said input memberV to said output member to drive Isaid output member in the sante direction;

' said first' an'dsecond drives having the 'same speed ratio and said,l thirdl drive having a higher speed ratio; a source offluidfunderpressure; andvalve means for connecting said source tojsaid first, second and third fluid `operated third drives and being Vvoperative in a first position for gv l, controlling .the supply of fluidfor fsaidrst, second and i 'i VVthird fluid operated means for disengaging said Vfirst, sec:`

ondand third drivesv and being'operative infra second .position for controlling the supplyofifluid forA said first,

secondjiandithirdfluid operated means forengaging said 'first drive` and includingjtime delay means operative to one-Way torque transmission having fluid operated means Y third drives having the same higher speed ratio; a source of fluid under pressure; valve means for connecting lsaid source to said first, second ,and third fluid operated Vmeans operative in a first position for controlling the 1 means tofengage and disengage said first, secondand l control thesuppl-y4 of fluid for said second fluid'operated f means to-engage said second drive' a predetermined time delay after engagement offsaid first fdriveggand for con- Y trolling the supply Vof'fluid fortsaidvthirdildrive, to disengage 4said fthird drive, being operative in 1a Vthird Vposif tion to control the supplyrpof fluid `for said first, second vand thirdtlluid -actuated'rmeans to disengage said lfirst and third 'drives'prand to; engage said second drivefand being A-olferativejin affourthfposition to control thesupply Vof fluid forsaid"first, secondiand third fluid operated meureV to ydi'sengagev said Vfirst' drh/eend t0 Cl'llge said second' 'f'andithirddrlv d Y Y l p ,A 8, `Inarrautom .'ctransmis'siongan input member; an-

',Outp

ember d meansinclu'ding a first-drive, pro`- l d f u-e` transmissionmaving 'nrstfiuid y means" operativeA i' second drive-providing `tivo-Way y torque transmission 'd pe ated means operativeffo'y yengag Y third drive'previstasany Y lll,v In an `automatic transmission; an input member;` 1 an output member; drive means ,including a first drive l Vhaving second fluid oper gaging said second drive, la third drivejprovidingionly v,one-,Way `torque transmission having fluid operated-,means supply of fluid to said rst, second andthird fluid operated means to engage said first drive and to -disengage said second and third drives and operative in a second position for controlling the supply of fluid to said first, second and third fluid operated means to disengage said first drive, to engage Said second andithird drives and including delay means for controlling the supply .of `fluid Vto said third fluid operated means to engage said third drive ka predetermined time kafter engagement of said second drive. 1 l Y v9. The invention defined in claim 8 vand said valve means being operative on movement `from said second position to said first position for flnstwcontrollingthe supply of fluid for said first and second fluid operated means to disengage said second drive and engage said first drive and including delay means operative after ka predetermined time delay to control the supply of fluid to said third fluid operated means to disengage said third drive to provide overlap.v

lO. In an `automatic transmission; Lan input member; an output member; drive means including a first drive providing two-'Way torque transmission having first fluid operated means operative for engaging said first drive, a second drive Vproviding rtwo-way torque transmission having second fluid operated means operativerfor engaging said second drive,V and a third driveV providing 'only one-Way torque transmission having fluid V.operated means operative for engaging said third drive; each of said drives connecting'said input member to said output member to drive said output member in the same direction, said first'drive lhaving a loW speed ratio, said second and third drives having the 'same higher speed ratio; a -V source of fluid under pressure; valve means connecting said source to Said first, second-and third fluid,y operated rneansooperative'in a first position for controlling -t-he supply of fluid to said first, second and third Afluid operated means to engage said first drive and disengageV said said first position to first control the supplyv of fluidV to said first, ,secondv and'thirdgfluid .operated means to disengage saidsecond and third drives andto engage said first drive and including time'delaymeans foridelaying disengagement ofV saidthirdi drive Ia predetermined time )after ydisengagement of said second drive to provide overlap.

providing tvvo-if/ay torque transmission having firstlfiuid operated means operative for engaging said first drive,

f'afsecond drive providing twoiwayl-torque 'transmission ated Vmeans:operative forV eni operative for engaging saidithird drive anda fourth drive providing ytvvo-vvay torque transmissionV having fourth j. fluid-operatedmeansfoperative for 'engaging saidfourth (drive,` [each ofsaid drives', connectingsaid'inputfmember ,i to V4,said outputfmernber yto',` drive said output'rnember in 1 the saine directiofn; said `first `drivefh-aving,a lowspeed i 4 aid `second and thirdldrives having the sameriihig'her ,Speed' -ratio;rsaid vfourth drive'having a still higher' speed K ratio; `afsource offluid finder pressure, and valve means ratio for connecting said source to said first, second and third fluid operated means operative in a first position for controlling the supply of fluid -to said first, second and third fluid operated means to engage said first drive and disengage said second and third drives, and in a second position for controlling the supply of fluid to said first, second and third fluid operated means to disengage said first drive `and to engage said second and third drives and including delay means operative for controlling the supply of fluid to said third fluid operated means to engage said third drive after a predetermined time delay and movable to a third position for lcontrolling the supply of fluid to said first, second `and third fluid .operated means -to disengage said first and second drives and to engage said third drive and means operative only when said manual valve means is in said third position for controlling the supply of fluid to said fourth fluid operated means to engage said fourth drive.

l2. In an automatic transmission; an input member; an `output member; drive means including a first drive providing two-Way torque transmission having first fluid operated means operative for engaging said first drive, a second drive providing two-'Way torque transmission having second fluid operated means operative for engaging said second drive, a third drive providing only one-Way torque transmission having fluid operated means operative for engaging said third ydrive and a fourth drive providing two-way torque transmission having fourth fluid operated means operative for engaging said fourth drive, each of said drives connecting said input member to said output member to drive said output member in the same direction, said first drive h-aving a lovv speed ratio, said second and third drives having the same higherV speed ratio; said fourth drive having a still higher speed ratio; a source of fluid under pressure, and valve means for connecting said source selectively to Ieach of said fluid operated means operative in a first position for controlling the supply of fluid to each of -said fluid operated means yto engage said first drive and disengage said second, third and fourth drives and in a second position for controlling the supply of fluid to each of said fluid operated means to disengage said first and four-th drives and to engage said` second and third drives and including delay means operative for .controlling the supply of fluid for said third fluid operated means to engage said third drive after a predetermined time delay and movable to a third position for controlling the supply of fluid to each of said fluid operated means to disengage` said first, second and fourth drives and to engage said third drive and means operative in a fourth position to control the supply of fluid to each of said fluid operated means to disp engage `said first and second drives rand to engage said third and fourth drives.

13.. In an automatic transmission; 'an input member;

one-Way torque transmission having fluidroperated` means operative `for engaging said third drive; each of said drives connecting said input member to said output member `to drive said output mem-ber inthe same direction, said firstdrive having a low speed ratio; said second and third drives having the same higher speed ratio; a source of fluid under pressure; valve means connecting said source to said first, second and `third fluid operated means operative in a first position for controlling the supply of fluid to said first, second `and third fluid operated means to engage said first drive and to disengage said second -and third drives and operative a second position for controlling the supply of fluid to said first, second and third fluid operated means to disengage said first drive, to engage `said second and third drives and including of the operator.

18 timing means for timing the engagement of said second `and third drives in a spaced time sequence.

14. In an automatic transmission; an inputmember; an output member; drive means including la first drive providing two-Way torque transmission having ,first fluid operated means operative for engaging said first drive, a second drive providing two-way torque transmission hav` ing second fluid operated means operative for engaging said second drive, and a third drive providing only oneway torque transmission having fluid operated means operative for engaging said third drive; each of said drives connecting said input member to said output member to drive said output member in the same direction, said first rive havin-g a lovvspeed ratio, said second and third drives having the same higher speed ratio; `a source of fluid under pressure; valve means connecting 4said source to said first, second and third fluid operated means operative in a first position for controlling the supply of fluid to said first, second and third fluid operated means to engage said first drive and disengage said second and third drives and in a second position operative for controlling the supply of fluid to said first, second and third fluid operated means to engage said second and third drive and to Vdisen-gage said first drive and operative on move-ment from said second position to said first position to rst control the supply of fluid to said first, second and :third fluid operated means to engage said first drive and to disengage said second and third drives and including timing means for timing the disengagement of said second and third drives in a spaced time sequence to .provide overlap during engagement of said first drive.

15'. In a transmission, input means, output means, fluid operated means connecting said input and output means to establish a driving connection between said input land output means, a source of fluid underpressure, mean-s connecting said source to said fluid operated means for establishing flow and releasing flow to operate said fluid operated `means including a passage having a restricting orifice operative during at least a portion of said mtablishing and releasing flow, and a one-Way bypass passage permitting only releasing flow connected in parallel to said restricting orifice to provide additional releasing flow capacity to increase the rate of release of said fluid operated means, and valve means controlling said bypass passage normally biased to a closed position and responsive to the speed of said output member to open said valve means permitting flow through at predetermined speeds.

1'6. In a transmission, an input member, an output member, fluid operated means :to establish a driving connection between said input `and output members, a source of fluid under pressure, supply mean-s to supply fluid from said source -to said fluid operated means including a re stricted and unrestricted passagelocated in parallel toV each other through which the fluid Aflows from said source to said fluid operated means, valve means insaid unrestricted passage biased to a closed position to control the fluid flow to said fluid operated means to control the fluid pressure in `said fluid operated means. lan accumulator consisting of a cylinder having -a piston |therein,.bia`sing means :biasing said piston in one direction, means connecting said controlled fluid pressure in said fluid operated means to said cylinder to Iactuate said piston in opposition to said biasing means, andmea-ns operatively connected to said piston to control said valve means.

17. The inventionV defined in claim 16 .and said biasing means including means to vary the biasing force at the will 18. In a transmission, an input member, an output member, fluidoperatedmeans -to establish a driving connection between said input and output members, a source of fluid under pressure, supply means to supply fluid from said source to said fluid operated means including a restricted and an unrestricted passage located in parallel to each other through which 4the fluid flows from said source said bypass passage Y is Y to lsaid liuid operated means valve means in said unrestricted passage lbiased to `a closed position and movable to Ian open position to control Ithe lluid flow to said fluid operated means to control the liuid pressure in said fluid operated means, `an laccumulator consisting of a cylinder having a piston therein, biasing means biasing said piston in one direction, means connecting said controlled fluid pressure in said fluid operated means to said cylinder to actuate said piston in opposition to said biasing means, and valve actuator means operatively connected to said piston and engages the valvemeans only during a predetermined range of movement to hold said valve means in `saidrunrestricted passage in said open position during a predetermined range of movement of said piston.

` l 19. In la transmission for a drive'mechanism havingran engine, control means responsive to the torque demand on an engine, an input member driven by .the engine, an output member, fluid operatedmeans to establish a drivin-g connection between said inputV and output members, a source of fluid under pressure, supply means to supply iiuid from said source to said iluid operated means includ-4 ing ra restricted and unrestricted passage located in parallel to each other through which thelluid liows from said source to said fluid operated means, valve means in one of said passages biased to a closedV position and movable to 1an open position to control the fluid liow to said fluid 4 Eb Y 22. In a transmission for a drive mechanism including an engine, control meansresponsive to the torque demand on the engine, an input member adapted to be driven by the engine, an output member, a fluid operated device to establish a driving connection between said input and output members, a source of fluid under pressure, a torque demand means movable by said control means to provide a torque demand pressure proportional to the torque de-y mand on said engine, governor means providing a governor pressure proportional to the speed of one of said members, means including a shift valve including a'first element connecting said fluid operated device to exhaust in a first position Iand connecting' said source to said fluid operated rdevice in a second position, a second element, said first and second elements being coaxially located in a first bore closed at both ends, a third element iocated in an independent coaxial second bore having a portion projecting into said first bore and engaging said second valve element, biasing-means in said second bore biasing ,said

operated means to control the liuid pressure in said iiuid l operated means, an accumulator consisting of a cylinder having a piston therein, lbiasing means including means operative in response to said control means to vvtary the biasing force in response to .the torque demand on said engine VVto bias said piston Vin one direction, means connectingsaid controlled liuid pressure in said liuid operated means to said cylinderrto lactuate said piston in opposition tosaid biasing means, @and means operatively connected to said piston `to control said valve means.

. `420. In a transmission, input means, output means, fluid operated means connecting said .input and output means to establish a driving connection between said input and output means, -a source of fluid under pressure, supply means connecting said source to said fluid operated means for establishing flow and releasing flow Vto operate said iluid operated moan-s including a rst passage having a restricted orifice operative during one portion of said establisbing and-releasing flow and an unrestricted passage operat-ive during another portion of said releasing llow, a one-way bypass passage permitting only" releasing lioW connected in parallel to said orifice to provide additional releasing flow capacity to increase theV rate of releasey ofl saidfluid loperated means, valve means controlling said bypass passage normally biased to `a closed position and responsive to the speedV of said output member to open said valve means permitting flowthrough said bypass passage, and means responsive yto the ypressure in said liuid operatedmeans to render said restricted or unrestricted passagein said first passage operative.

21. Inlaftransrnissionfora drive mechanism having an engine, control means responsive to the torque demand of an engine, input means `driven by `an engine,` output means, fluid operated-means connecting said input and output means to establish -a `drivingconnection between said input and output means, `a source of iin-idV under pressure, means connecting said source to said fluid operated means for establishing flow yand releasing ilow to 'operate t said fluid operated means including a restricted orifice operative during vat least a portion of said establishing and releasing flow, a one-way bypass passage connected in parallel to `said orifice to provide additional release flow capacity to increase the rate of release of said fluid operated means, and valve means controlling said bypass passage normally biased proportional to the torque demand by said control means to a .close-'d position and movable responsive to high speed of Ysaid output member to open said valve means permitting flo-w through said bypass passage. Y'

third valve element portion into engagement with said second lValve element to bias said valve elements in one direction, said governor pressure being connected to said first bore to urge said rst valve element in the opposite direction and to said second `bore to urge said third valve element in said opposite direction, said torque demand pressure being connected to said first bore between ,said first and second valve elements in said first position of said first valve element yand disconnected in said second position of said first valve element and being connected between said second valve element and said projection on said thirdvalve element to under partial torque demand conditions hold said lir'st valve element in said first position `against said governor pressure and to lassist said governor pressure to move said 4third valve element against said spring away from said first valve element to provi-de rateless operation of said first valve element on the shift from said first to said second position.

23. Infan automat-ic transmissionpan input member, an output-member, a lowand 'a high ratio control device to establish la low `and high drive ratio between said input and output members, detent means to provide a force at the will of the operator, governor means providing va governor force proportionai to the speed of said transmission, automatic control means responsive to said governor force Vto selectively establish said Vlow and high ratio control device to establish said low or high ratio, said detent `rnetnis; t being operatively, connected to said automatic control means to position said automatic control means in said low ratio position, and means responsive to the establish-,

high drive ratio between said input and output members,A

a source'of fluid under pressurejtorquemeans operable l1n response to said torque control means to provide a y torque pressure proportional tothe torque demand, de-

tent means to provide a pressure at the Willof the operatory higher than :said torquepressure,'governor means providing la governortpressure Vproportional to the speed of said transmission, automatic control means responsive to said governor pressure and said torque pressure to selectively connect said source to said low and high liuid oper- Y ated ratio device to establish said low or a high ratio, said detent means being operatively connected to said automatic control means to position said automatic control means in said low ratio position, and means responsive to the pressure in Vsaid highrratio iiuid operated device acting on :said detent means to` signal the operator so that the fil operator will be infomed when operation of the detent means is effective to downshift the transmission.

25. In a control mechanism -for -a hydraulically operated transmission; a supply line; firstcontrol means; a source of fluid under pressure; ia first signal means movlable by said first control means to provide `a rst signal pressure proportional to afunction of said first control means, second control means, a second signal means proviidng a second signal pressure proportional to a function of said second control means; means including a shift valve including la first element connecting said supply line to exhaust in a first position and correcting said source to said supply line in la second position, a second element, said first and second elements being coaxially located in `a first bore closed at both ends, a third element located in au independent coaxial second bore having a portion projecting into said first bore and engaging said second valve element, biasing means in said second bore biasing said third valve element portion into engagement with said second valve element to bias said valve elements in one direction, said second signal pressure being connected to said first bore to urge said first valve element in the opposite direction and to said second bore to urge said third valve element in said opposite direction, said first signal pressure being connected to said first bore between said first and second valve elements in said first position of said first valve element and disconnected in lsaid second position 'of said first valve element and being connected between said second valve lelement and said projection on said third valve element to under partial first signal conditions hold said -first valve element in said first position against said second signal pressure and to assist said second signal pressure to move said third valve element against said spring away from said first valve element to provide rateless operation of said first valve element on the shift from said first to said second position.

26. ln a governor control system for la transmission; first control means; a fluid ope-rated device; a source of fluid under pressure, first signal means movable by said first control means to provide a first signal pressure proportional to a function of said first control means; governor means providing la governor pressure proportional to speed, means including a shift valve including a flrst element connecting said fluid operated device to exhaust in a rst position .and connecting said source to said fluid operated device in a second position, a second element, said first and second elements being coaxially located in a first ,bore closed at both ends, a third element located in yan independent coaxial second bore having a portion projecting into said first bore and engaging said second valve element, biasing means in said second bore biasing said third valve element portion into engagement with said second valve element to bias said valve element-s in one direction, said governor pressure being connected to said first bore to urge said first valve element in the opposite direction and to said second bore to urge said third valve element in said opposite direction, said first signal pressure being connected to said first bore between said first and second valve elements in said first position of said first Valve element and disconnected in said second position of said first valve element land being connected between said second valve element and said projection on said third valve element to under partial first signal conditions hold said first valve element in said first position against said governor pressure 'and to assist vsaid governor pressure to move said third valve elements against said spring away from said first valve element to provide rateless operation of said first valve element on the shift from said first to said second position.

27. In a transmission for a drive mechanism including an engine, control means responsive to the torque demand on the engine, an input member adapted to be driven by the engine, an output member, a fluid` operated device to establish a driving connection between said input and output members, a `final drive member driven by said output member, a source lof 4fluid under pressure, a torque demand means movable by said control means to provide a torque demand pressure proportional to the torque demand on said engine, governor means including governor fluid supply means providing a governor pressure proportional to the speed -of one of said final drive members, means including a shift valve including a first` element connecting said fluid operated device to exhaust in a first position and connecting said source to said fluid `operated device in asecond position, la second element, said first and secondelements being coaxially located in a first bore closed at both ends, a third element located in an independent coaxial second bore having a portion projecting into said first bore and engaging said second valve element, biasing means in said second bore biasing said third valve element portion into engagement 'with said second valve element .to bias said valve elements in one direction, means connecting said governor means to urge said first valve element in the lopplosite direction, and means connecting said governor fluid supply means to said second bore to supply governor pressure to urge said third valve element in said opposite direction, said torque demand pressure being connected to said first bore between said first and second valve element-s in said first position of said rst valve element and disconnected in said second position of said first valve element land being connected between said second valve element and said projection on said third valve element to under partial torque demand conditions hold said first valve element in said first position against said governor means and to assist said governor pressure supplied by said governor fluid supply means to move said third valve elements lagainst said spring away from said first valve element to provide rateless operation of said first valve element on the shift from said first to said second position.

28. In .a transmission, drive means provi-ding -a .low and a high ratio drive, control means operatively connected to said drive means to selectively establish said low and high ratio drive, operator controlled means including lan operator controlled valve element operatively connected to said control means and actuable to control said control means to insure operation of said drive means in said low ratio, and means connected to said control means and operator controlled means providing a fluid pressure acting directly on said operator control valve element only when said drive means is in high ratio to signal the operator only -when said operator controlled means is effective lto downshift the transmission.

29. In a transmission; input means; output means; fluid operated drive means connecting said input and output mean-s to establish a driving connection between said input and output means; a source of fluid under pressure; shift valve means including first conduit means connecting said source -to said shift valve and second conduit means connecting said shift valve to said fluid operated means; said shift valve being operative in one position to connect said source through said first conduit means, shift valve and second conduit means to said fluid operated means Aand in another position to connect said fluid operated means through said second conduit means and shift valve to exhaust; said second conduit means connecting said shift valve to said fluid operated means for establishing flow and releasing `flow to operate said fluid operated means including a first passage having a restricting orifice operative during at 'least a portion of both said establishing and releasing flow, anda one-way bypass passage permitting `only releasing flow connected in parallel to said restricting orifice to provide Iadditional releasing flow capacity to increase the rate of release of said fluid operated means, and means to selectively block said oneway bypass passage during releasing flow through said first passage to selectively control the rate of releasing ilovv.

30. The invention defined in claim 29, and said means to block `said one-Way bypass passage being operative to block said releasing 110W at 10W transmission speeds.

References Cited inthe iile of this patent UNITED STATES PATENTS 5 Y Burtnett Apr. 15, 1952 lMcFarland May 6, 1952 Dodge Aug. 12, 1952 Y McRae Jan. 6, 1953 Westbury et a1. 51m@ 3o, 1953 10 VMcFarland Oct. 19, 1954 Kelbel etal. Nov. 9, 1954 Snyder June 19, 1956 Collins uly 31, 1956 Rosenberger Oct. 16, 1956 Sheppard Apr. 16, 1957 Christensen May 21, 1957 v Foster Oct. 1,- 1957 Kelley Jan. 7, 1958 De Lorean Feb. 17, 1959 Holdeman et al.Y Iu1y'21, 1959 Bolrman Ia.n.5,'1960v 

1. IN AN AUTOMATIC TRANSMISSION; AN INPUT MEMBER; AN OUTPUT MEMBER; DRIVE MEANS INCLUDING A FIRST DRIVE PROVIDING TWO-WAY TORQUE TRANSMISSION HAVING FIRST FLUID OPERATED MEANS OPERATIVE FOR ENGAGING SAID FIRST DRIVE, A SECOND DRIVE PROVIDING ONLY ONE-WAY TORQUE TRANSMISSION HAVING SECOND FLUID OPERATED MEANS OPERATIVE FOR ENGAGING SAID SECOND DRIVE, AND A THIRD DRIVE PROVIDING TORQUE TRANSMISSION HAVING FLUID OPERATED MEANS OPERATIVE FOR ENGAGING SAID THIRD DRIVE; EACH OF SAID DRIVES CONNECTING SAID INPUT MEMBER TO SAID OUTPUT MEMBER TO DRIVE SAID OUTPUT MEMBER IN THE SAME DIRECTION; SAID FIRST AND SECOND DRIVES HAVING THE SAME SPEED RATIO AND SAID THIRD DRIVE HAVING A HIGHER SPEED RATIO; A SOURCE OF FLUID UNDER PRESSURE; VALVE MEANS FOR CONNECTING SAID SOURCE TO SAID FIRST AND SECOND FLUID OPERATED MEANS TO ENGAGE AND DISENGAGE SAID FIRST AND SECOND DRIVES AND BEING OPERATIVE IN A FIRST POSITION FOR CONTROLLING THE SUPPLY OF FLUID TO SAID FIRST AND SECOND FLUID OPERATED MEANS FOR DISENGAGING SAID FIRST AND SECOND DRIVES AND BEING OPERATIVE IN A SECOND POSITION FOR CONTROLLING THE SUPPLY OF FLUID TO SAID FIRST AND SECOND FLUID OPERATED MEANS FOR ENGAGING SAID FIRST DRIVE AND INCLUDING TIME DELAY MEANS OPERATIVE FOR CONTROLLING THE SUPPLY OF FLUID TO SAID SECOND FLUID OPERATED MEANS FOR ENGAGING SAID SECOND DRIVE A PREDETERMINED TIME AFTER ENGAGEMENT OF SAID FIRST DRIVE AND BEING OPERATIVE IN A THIRD POSITION FOR CONTROLLING THE SUPPLY OF FLUID TO SAID FIRST AND SECOND FLUID ACTUATED MEANS TO DISENGAGE SAID FIRST DRIVE AND TO ENGAGE SAID SECOND DRIVE; AND MEANS FOR CONTROLLING THE SUPPLY OF FLUID TO SAID THIRD DRIVE FOR ENGAGING AND DISENGAGING SAID THIRD DRIVE OPERATIVE ONLY WHEN SAID VALVE MEANS IS IN SAID THIRD POSITION TO CONTROL THE SUPPLY OF FLUID TO SAID THIRD FLUID OPERATED MEANS TO ENGAGE SAID THIRD DRIVE. 